Patent Application
20220152806
According to the present disclosure, there is provided an apparatus and method as set forth in the appended claims. Other features of the invention will be apparent from the dependent claims, and the description which follows.
Accordingly, there may be provided a power tool having an operational axis, the power tool comprising: a tool carrier for mounting an impact tool, the tool carrier comprising: a base member aligned with the operational axis, the base member having: a head end for receiving impact energy; a foot end at an opposite end of the tool carrier, the foot end being provided with a tool mount configured to transmit the impact energy to a tool; and a casing engagement feature provided between the head end and foot end; and a first casing module, at least part of the tool carrier being located within the first casing module; the casing module being provided with a tool carrier engagement feature complementary in shape to and for interlocking engagement with the tool carrier casing engagement feature to thereby: prevent rotation of the tool carrier relative to the first casing module around the operational axis, and permit relative movement between the tool carrier and the first casing module along the operational axis.
There may also be provided a power tool having an operational axis, the power tool comprising: a tool carrier for mounting an impact tool, the tool carrier comprising: a base member aligned with the operational axis, the base member having: a head end for receiving impact energy; a foot end at an opposite end of the tool carrier, the foot end being provided with a tool mount configured to transmit the impact energy to a tool; and a casing engagement feature provided between the head end and foot end; and a first casing module, at least part of the tool carrier being located within the first casing module; the casing module being provided with a tool carrier engagement feature complementary in shape to and for interlocking engagement with the tool carrier casing engagement feature to thereby: prevent rotation of the tool carrier relative to the first casing module and around the operational axis, and permit relative movement between the tool carrier and the first casing module along the operational axis.
The tool carrier casing engagement feature may comprise a fin which: extends radially outward from the tool carrier base member; and extends longitudinally along the length of the tool carrier base member such that, in use, the fin is aligned with the operational axis of the power tool.
The tool carrier casing engagement feature may further comprise a web plate which extends from an end of the fin around a circumference of the main member.
The first casing module engagement feature may be provided as a groove configured to receive the fin of the tool carrier casing engagement feature, the groove being aligned with the operational axis of the power tool; and configured to permit the tool carrier to move relative to the casing module along the operational axis.
The power tool may further comprise an actuator module centered on the operational axis; the actuator module having: a plurality of rods held in a fixed relationship to one another by: a mounting member toward one end of the rods, and a coupling member spaced apart from the mounting member toward an opposite end of the rods; the actuator module being coupled to the first casing module via the coupling member; and the coupling member is further provided with an aperture through which the head end of the tool carrier extends.
The power tool may further comprise a carrier mount for engagement with a carrier, the carrier mount being coupled to the end of the mounting member of the second casing module.
A second casing module may extend between the mounting member and the coupling member.
The actuator module may further comprise: a body, and an actuator for moving the body along the operational axis of the power tool: from an impact position at which the body is operable to transfer impact energy to the head of the tool carrier to a retracted position distal to the impact position and proximate to the mounting member.
The actuator may comprise a housing which extends from the carrier mount end of the power tool along the operational axis part way along the length of the second casing module within a volume defined between the plurality of rods.
The body may comprise: an actuator channel which extends from a head end of the body to a foot end of the body, the head end of the body facing the carrier mount end of the power tool, the foot end of the body facing the head end of the tool carrier, such that when the body travels between the retracted position and the impact position, a clearance is maintained between the actuator housing and the body.
The actuator channel may terminate in a hammer plate configured to strike the head end of the tool carrier.
The actuator may be a hydraulic or pneumatic ram comprising a piston.
The ram piston may be provided with a clutch mechanism for selectively engaging with the body, and arranged such that: at the impact position the clutch mechanism is operable to couple the body to the piston; the clutch is operable to couple the body to the piston while the body is carried by the piston to the retracted position; and at the retracted position the clutch mechanism is operable to uncouple the body from the piston, permitting the body to move on an impact stroke to the impact position substantially without hindrance from the piston.
The body may define passages in slideable engagement with at least some of the rods; configured such that the body may translate between the impact position and the retracted position along at least some of the rods.
The body may have a greater mass than mass of the tool carrier, or may have a greater mass than the combined mass of the tool carrier and tool assembly.
The power tool may further comprise of an array of elastic ropes, one end of the array of elastic ropes being coupled to the body, and another end of the elastic ropes being coupled to the coupling member; configured such that the body may translate from the impact position to the retracted position in a first direction along at least some of the rods under the action of the actuator and against the force developed by the elastic ropes; and wherein the body is biased to move in a second direction along at least some of the rods toward its impact position from its retracted position by the elastic ropes whilst uncoupled from the actuator.
The ropes may be coupled via a direct load transmission path to the coupling member and body.
At least one of the ropes may comprise a solid rubber core member.
The at least one rope may be provided with a body end cap at one end for engagement with the body; and a coupling member end cap at its other end for engagement with the coupling member, a largest external diameter of the body end cap being greater than the largest external diameter of the coupling member end cap.
The end caps may be joined to the rope by an adhesive.
The body may comprise a rope passage which extends from a head end of the body to a foot end of the body, at least one of the ropes extending through the rope passage.
The head end of the rope passage may comprise a restriction having an internal diameter less than the maximum external diameter of the body end cap, and greater than the maximum external diameter of the coupling member end cap such that, during assembly, the coupling end cap and rope can be entered in the head end of the rope passage, passed along the rope passage and extend out of the foot end of the rope passage so that the body end cap is caught in the head end of the rope passage; and the coupling member end of the rope may be attached to the coupling member.
The body end cap may be tapered along its length.
The second casing module may comprise an access panel located to enable access to the head end of the body to facilitate the insertion and removal of a rope from the rope passage.
The coupling end cap of the rope may comprise: a locking shoulder or slot; the coupling member comprises rope apertures through which the coupling member end cap extends; the coupling member comprises slots which extend from the rope apertures to a radially outer surface of the coupling member; and each slot is provided with a locking fork which is slidable within the slot such that when the coupling end cap extends through the rope aperture in the coupling member, the locking fork may be slid to engage with the locking shoulder or slot to thereby lock the end cap to the coupling member; and the locking fork may be slid to disengage with the locking shoulder or slot to thereby release the end cap from the coupling member.
The coupling member slot may have a first region having a first width radially inward of a second region having a second width narrower than the first width; and the fork has a main body region and a neck region, the second region of the slot being narrower than the main body region of the fork, such that the fork is retained and slidable within the slot.
A first damper may be provided between the coupling member and the tool carrier.
The first damper may comprise at least two damping members in series along the operational axis.
The at least two damping members may have different stiffness to one another.
A second damper may be provided between the tool carrier and a foot end of the first casing module.
The second damper may comprise at least one fluid damper.
There may also be provided a method of applying a percussive force to an object, using a power tool as claimed in any preceding claims.
Thus there is provided a power tool having many advantages over related art devices.
For example, it provides a tool carrier that will not twist with respect to the rest of the power tool, hence ensuring any attached cutting tool remains correctly aligned. The power tool of the present disclosure also produces less noise and less vibration, which is of importance to a tool operator and anyone else in the vicinity of where the tool is being operated. It also manages forces arising during a “mis-fire” of the tool better than a device of the related art. Hence, a device according to the present disclosure is an improvement in many ways over devices of the related art.
Examples of the present disclosure will now be described with reference to the accompanying drawings, in which:
The power tool 30 comprises a tool carrier 34 for mounting (that is to say, supporting or carrying) an impact tool 36. One example of an impact tool 36 is shown mounted on the end of the tool carrier 34 is shown in
The tool carrier 34 is shown in more detail in
The power tool 30 further comprises a first casing module 50, where, as shown in
As best shown in
The casing module engagement feature 52 comprises a groove 52 configured to receive the fin 54 of the tool carrier casing engagement feature 46. In the example shown, several grooves 52 are provided, spaced around the inner surface of the first casing module 50 such that each groove 52 receives one of the fins 54 of the tool carrier casing engagement feature 46. Each groove 52 is aligned with (that is to say, parallel and orientated in the same direction as) the operational axis 32 of the power tool 30. That is to say, the grooves 52 are parallel to, and offset from, the operational axis 32.
Thus, the fins 54 are located in the grooves 52 so as to prevent rotation of the tool carrier 34 relative to the first casing module 50 around the operational axis 32. That is to say, the fins 54 are located in the grooves 52 so as to prevent rotation of the tool carrier 34 relative to the first casing module 50, and to prevent rotation of the tool carrier 34 around the operational axis 32. However, the fins 54 are also slidable within the grooves 52 to enable relative movement between the tool carrier 34 and the first casing module 50 along the operational axis 32. That is to say, the groove 52 seats and locates the fin 54, so that the tool carrier 34 cannot move relative to the first casing module 50 around the operational axis 32. Put another way, the groove 52 seats and locates the fin 54 so that the tool carrier 34 cannot rotate around the operational axis 32 relative to the first casing module 50, and so that the tool carrier 34 cannot rotate around the operational axis 32. That is to say, since the groove 52 seats and locates the fin 54 so that the tool carrier 34 cannot rotate relative to the first casing module 50, and since the first casing module is non-rotatable around the operational axis, the engagement of the groove 52 and fin 54 ensures that the tool carrier 34 is non-rotatable around the operational axis 32. However, because each fin 54 is slidably located in its respective groove 52, the tool carrier 34 is operable to move in a direction along (or parallel) to the operational axis 32 by virtue of the fact that the fins 54 are carried within their respective grooves 52.
The power tool 30 further comprises an actuator module 60 centered on the operational axis 32. The actuator module 60 has a plurality of rods 62, spaced apart from, and parallel with, one another and the operational axis 32 to form a “squirrel cage”. In the example shown, four rods 62 are provided. However, the power tool 30 may comprise more than four rods 62. The rods 62 are held in a fixed relationship with respect to one another by a mounting member 64 toward, or at, one end of the rods 62, and a coupling member 66 spaced apart from the mounting member 64 toward an opposite end of the rods 62. The actuator module 60 further comprises a second casing module 68 which extends around the rods 62, and also extends between the mounting member 64 and the coupling member 66. The second casing module 68 is coupled to the first casing module 50 via the coupling member 66. That is to say second casing module 68 is coupled (for example bolted) to the first casing module 50, with the coupling member 66 interspaced, and hence clamped, between the ends of the first casing module 50 and the second casing module 68.
Alternatively or additionally, the casing module 68 may be formed integrally with, or separately from, one or more of the mounting member 64 and coupling member 66.
As shown in the
The power tool 30 may further comprise a carrier mount 72 for engagement with a carrier (not shown). The carrier may take the form of a vehicle, for example a backhoe loader. As shown in
The actuator module 60 further comprises a body 80 and an actuator 82 for moving the body 80 along the operational axis 32 of the power tool 30. The actuator 82 is operable to move the body 80 in a first direction (indicated by arrow “B” in
The body 80 comprises an actuator channel 86 which extends from a head end 88 of the body 80 to a foot end 90 of the body 80. The head end 88 of the body 80 faces the carrier mount 64 end of the power tool 30. The foot end 90 of the body 80 faces the head end 40 of the tool carrier 34. The actuator channel 86 is sized relative to the size of the cylinder housing 84 of the actuator, such that there is a clearance between the actuator housing 84 and the body 80. Hence, when the body 80 travels between the retracted position and the impact position, a clearance is maintained between the actuator housing 84 and the body 80.
The actuator channel 80 terminates in a hammer plate 100 configured to strike the head end 40 of the tool carrier 34.
The ram piston is provided with a clutch mechanism 110 for selectively engaging with the body 80, and arranged such that during a return stroke to the retracted position (as shown in
The body 80 defines passages 116 in slidable engagement with at least some of the rods 62. The passages 116 are configured such that the body 80 may translate between the impact position and the retracted position at least along some of the rods 62. In the example shown, the body 80 is carried on, and slides along, all of the rods 62.
The body 80 has a greater mass than the mass of the tool carrier 34. The body also has a greater mass than the mass of the tool carrier 34 and tool assembly 36. That is to say, the body has a greater mass than the combined mass of the tool carrier 34 and tool assembly 36.
As shown in
The ropes 120 are shown in more detail in
At least one of the ropes comprises a solid rubber core member 130. The solid core member 130 may comprise a middle section 131 of substantially uniform thickness. That is to say, it may have substantially uniform diameter in a non-extended state and when extended. The solid core member may also be provided with ends 133 which have a greater thickness (i.e. diameter) than the middle section 131. The ends 133 may be frusto-conical. That is to say, the solid core member 131 may increase in diameter/thickness along at least part of the length of the core member 131 toward the ends 133.
The rope may be made from neoprene or natural rubber.
This composition may provide a rope which can stretch at least 1.6 times (i.e. 160%) its non-extended (i.e. at rest) length, with an upper elastic limit of three times (i.e. 300%) its non-extended (i.e. at rest) length.
Each rope 130 may be provided with a body end cap 132 at one end for engagement with the body 80, and a coupling member end cap 134 at its other end for engagement with the coupling member 66. The largest external diameter of the body end cap 132 is greater than the largest external diameter of the coupling member end cap 134.
The end caps 132, 134 are pushed over the ends 133 of the core member 130, such that ends 133 are received in a chamber (or “cavity”) formed within the end caps 132,134. The geometry of the end cap cavity is complementary in shape to the geometry of the rope ends 133 to trap the end caps 132, 134 onto the rope core member 130. An important feature is that the end caps 132, 134 are not crimped around the rope ends 133, as this would generate a stress raising feature which may shorten the operational life of the rope assembly 120.
An adhesive 136 may also be provided between the solid rubber core member 130 and the material of the end caps 132, 134.
The solid core member 130 may be provided as the only elastic and extendable part of the rope. That is to say, no sheath or braiding may be provided around the solid core member 130. The reason for this is best understood with reference to conventional elastic ropes, which comprise a braided sheath. The sheath is essential to such rope types to protect the elastic fibers from abrasion (e.g. when being uncoiled, or pulled over surfaces). The sheath moves with the elastic fibers as the rope extends and contracts. Once the sheath is fully extended, the rope cannot extend any further.
By contrast, the ropes of the present disclosure comprise solid rubber core members 130, which inherently do not need retaining by a sheath. Neither do they require a sheath to prevent abrasion as they are positioned and mounted such that abrasion is unlikely. Also, the absence of a sheath means the ropes may stretch further relative to their non-extended state, and hence store more energy, than a braided rope could achieve.
The ropes 120 are not pre-loaded. That is to say, in a non-extended state, no energy is stored in the ropes 120.
As shown in
The body 80 comprises a rope passage 140 which extends from the head 88 of the body 80 to a foot end 90 of the body 80, where the head end 88 of the body 80 faces the mounting member 64 end of the power tool 30, and the foot end of the body 80 faces the head end 40 of the tool carrier 34. At least one of the ropes 120 extends through at least one of the rope passages 140.
The head end of the rope passage 140 comprises a shoulder or restriction having an internal diameter less than the maximum external diameter of the body end cap 132. The shoulder/restriction also has an internal diameter greater than the maximum external diameter of the coupling member end cap 134. Hence, during assembly, the coupling end cap 134 and core member 130 can be entered into the head end of the rope passage 140, passed along the rope passage 140, and extend out of the foot end of the rope passage 140 so that the body end cap 132 is caught in by the restriction at the head end of the rope passage 140, and the coupling member end cap 134 of the core member 130 may be attached to the coupling member 66.
The second casing module 68 comprises an access panel 150 located to enable access to the head end 88 of the body 80 to facilitate the insertion and removal of a rope 120 from the rope passage 140.
The coupling member 66 comprises rope apertures 154 (not shown) through which the coupling member end cap 134 extends. The coupling member 66 comprises slots 156 which extend from the rope apertures 154 to a radially outer surface of the coupling member 66. Each slot is provided with a locking fork 158 which is slidable within the slot 156 such that when the coupling end cap 134 extends through the rope aperture 154 in the coupling member 66, the locking fork 158 may be slid to engage with the locking shoulder 152 or slot 152 to thereby lock the end cap 134 to the coupling member 66. The locking fork 158 may be slid to disengage with the locking shoulder 152 or slot 152 to thereby release the end cap 134 from the coupling member 66.
As shown in
The elastic ropes 120 are configured such that the body 80 may translate from the impact position to the retracted position in the first direction (indicated by arrow “B” in
As shown in
As shown in
The power tool is operable to apply a percussive force to an object, for example a mass of masonry or a structure to be broken up.
In normal operation, a tool 36 is attached to the tool carrier 34, and the tool 36 is pressed into contact with a substantial mass/object. The clutch 110 is engaged to couple the body and actuator 82. The actuator 82 then draws the body 80 to the retracted position in the first direction (indicated by arrow “B” in
When retracted to a predetermined position, (as shown in
The body 80 is then drawn at high speed by the ropes 120 to move in the second direction (indicated by arrow “C” in
The force is transmitted by the tool carrier 34 to the tool 36, and hence the object to be broken up. The actuator 82 is then extended toward the body 80 so that the clutch 110 couples the body 80 and actuator 82, and the cycle starts again.
In the event that the tool 36 is not in contact with a target, for example, if the target has collapsed and/or the position of the target has shifted relative to the tool, it is possible for a “misfire” to occur. In such a scenario the body 80 strikes the tool carrier 34, and the tool carrier 34 is moved along rods 62, but the tool has no target to impart the force to.
In such a scenario, the web 56 of the tool carrier 34 strikes the second damper 180, placed as it is between the tool carrier web 56 and the first casing module, and the force is absorbed by the second damper 180. If only some of the impact energy has been absorbed, the tool carrier 34 may then rebound back along rods 62 and operational axis 32, such that the web 56 collides with the first damper 170 to absorb a further proportion of the energy. The tool carrier 34 may rebound further to strike the shock absorber 180, and again bounce back to hit the first damper 170 until all of the energy imparted to the tool carrier 34 is absorbed.
Thus the first damper 180 at the foot end of the power tool 30 arrests movement of the tool carrier 34 when no load is applied to the tool 36. In the example shown the first damper 180 is provided as a shock absorber 180, as described above. This is advantageous over, and not equivalent to, a solid rubber damper, since a ram-type shock absorber is compressed over a greater distance, and thus absorbs energy over a longer time period, which thus provides additional damping. Additionally, multiple shock absorbers, as shown in the device of the present disclosure, provide greater damping ability than, for example, a rubber shock absorber block.
A device of the present disclosure is thus advantageous since it provides a device having a substantially greater energy output per unit weight than either a purely pneumatic drill or the device as shown in
Since the power tool 30 of the present disclosure is inherently more efficient, the carrier vehicle, which provides power to the tool 30, may operate at a lower engine power setting than would be required with a power tool of the related art, thereby extending the life of the carrier vehicle, and reducing fuel consumption.
In examples where the actuator 82 is operated by hydraulic fluid delivered from a carrier vehicle, a power tool according to the present invention will require less work to be done by the fluid, and expose the fluid to less vibration, thus extending the life of the hydraulic fluid.
Additionally, the multiple (i.e. four) rod 62 support structure, in combination with passages for the rods extending the full length of the body 80, provides an improved bearing surface for the body 80 to slide along, increases stability of body 80 as it moves along the rods 42, and hence decreases vibration during the impact and retraction strokes.
Additionally, the body 80 is made as large as possible for the volume available in the casing of the power tool, thereby providing a larger momentum, and hence force, to strike the tool carrier 34.
The power tool of the present disclosure also includes an advantageous damping system including a first damper 170 and second damper 180 which are operable to absorb shock loads imparted to the tool carrier 34 during a misfire. This is extremely important as it prevents vibration and loads being transmitted to the casing of the power tool 30 and hence to the vehicle carrying the power tool 30. Since the carrier vehicle is exposed to less vibration and shock loads, the life of its components are increased. Additionally, the operator of the carrier vehicle is more comfortable, and hence can operate the device more effectively.
The fins 54 in conjunction with the grooves 52 of the tool carrier and casing 50 respectively prevent the tool carrier 34 from twisting relative to the power tool. That is to say, the fins 54 in conjunction with the grooves 52 of the tool carrier and casing 50 respectively prevent the tool carrier 34 from twisting relative to the casing modules of the power tool and, since the casing modules are non-rotatable around the operational axis 32, prevent the tool carrier 34 from twisting relative to the operational axis 32. This is extremely advantageous as it ensures a correct orientation of the end of the tool 36 attached to the tool carrier 34.
The modular nature of the power tool 30 makes it easier to assemble, re-configure and maintain.
The tool carrier 34 also allows for easy replacement of tools 36, for example to achieve a different cutting operation, or to replace a damaged tool 36.
Although the figures of the present application show a jack hammer type tool, the power tool of the present disclosure may form part of any power tool where it is required to deliver a cyclic percussive force to a target object.
Attention is directed to all papers and documents which are filed concurrently with or previous to this specification in connection with this application, and which are open to public inspection with this specification, and the contents of all such papers and documents are incorporated herein by reference.
All of the features disclosed in this specification (including any accompanying claims, abstract and drawings), and/or all of the steps of any method or process so disclosed, may be combined in any combination, except combinations where at least some of such features and/or steps are mutually exclusive.
Each feature disclosed in this specification (including any accompanying claims, abstract and drawings) may be replaced by alternative features serving the same, equivalent or similar purpose, unless expressly stated otherwise. Thus, unless expressly stated otherwise, each feature disclosed is one example only of a generic series of equivalent or similar features.
The invention is not restricted to the details of the foregoing embodiment(s). The invention extends to any novel one, or any novel combination, of the features disclosed in this specification (including any accompanying claims, abstract and drawings), or to any novel one, or any novel combination, of the steps of any method or process so disclosed. We claim:
| Number | Date | Country | Kind |
|---|---|---|---|
| GB1604758.1 | Mar 2016 | GB | national |
| PCT/GB2017/050773 | Mar 2017 | GB | national |
This application is a Continuation of U.S. patent application Ser. No. 16/071,415, entitled “Power Tool,” by Ian Webster, filed in the U.S. Patent and Trademark Office on Jul. 19, 2018 as a U.S. National Phase Application of PCT/GB2017/050773, which was filed on Mar. 20, 2017 with the International Bureau, and which in turn claims priority to foreign application number GB1604758.1, filed on Mar. 21, 2016, the disclosures of which are hereby incorporated by reference herein in their entirety. Pneumatic drills for cutting masonry are well known. Typically, they incorporate a weight which is raised against gravity by a hydraulic ram and when the weight has been raised to the desired extent, the weight is allowed to fall under gravity to strike a drill bit, delivering an impact force to a masonry target. FIG. 1 shows an alternative power tool as described in GB2375319B (BACA Limited). The tool 1 comprises a cuboid structural casing 2 to carry upper handles 4,6, and a work piece 8 in the form of a chisel. Inside, and further supported by, the casing there is a hydraulic ram 10 mounted through a platform 12. The ram comprises a cylinder 14 and a piston 16. Mounted onto a moving platform 18 there is a body 20 in the form of a heavy weight. Mounted between the moving platform and the bottom wall of the jackhammer are two elastic ropes 22,24 and shock absorbers 26,28. The jackhammer is shown in a vertical orientation with the chisel lower-most at the foot of the jackhammer. The moving platform 18 slides on the exterior surface of the ram cylinder 14. This necessitates the need for the external surface of the ram cylinder 14 to be machined to a close tolerance. It also introduces extra loads and wear on the ram cylinder. If the moving platform is not aligned correctly on the ram, its movement along the ram cylinder may create unwanted vibration. Additionally, since the casing 2 is structural, with the other tool components being mounted off the casing 2, it comprises a casting of robust and heavy design. Hence, the casing contributes significantly to the overall weight of the power tool. Although such devices may in practice be moved by a machine (for example coupled to an arm of a backhoe loader), they will inevitably need to be manhandled at some point. Hence, a power tool which provides the advantages of the device of FIG. 1, delivers a higher impact force per unit weight of the power tool, and yet reduces wear and load on the ram cylinder, is highly desirable.
| Number | Date | Country | |
|---|---|---|---|
| Parent | 16071415 | Jul 2018 | US |
| Child | 17592320 | US |
